US4706705A - Check valve - Google Patents
Check valve Download PDFInfo
- Publication number
- US4706705A US4706705A US06/846,962 US84696286A US4706705A US 4706705 A US4706705 A US 4706705A US 84696286 A US84696286 A US 84696286A US 4706705 A US4706705 A US 4706705A
- Authority
- US
- United States
- Prior art keywords
- axially
- guide sleeve
- valve seat
- valve
- ball
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/04—Check valves with guided rigid valve members shaped as balls
- F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
- F16K47/01—Damping of valve members
- F16K47/011—Damping of valve members by means of a dashpot
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7504—Removable valve head and seat unit
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/785—With retarder or dashpot
- Y10T137/7852—End of valve moves inside dashpot chamber
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7866—Plural seating
- Y10T137/7867—Sequential
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
- Y10T137/7922—Spring biased
- Y10T137/7927—Ball valves
- Y10T137/7928—With follower
Definitions
- This invention relates generally to check valves employed to provide generally unidirectional flow through a fluid passageway. More particularly, the present invention relates to miniaturized check valves of a type which employs a spring biased ball to control the fluid flow through the valve.
- the present invention is a new and improved check valve or relief valve of compact form wherein the valve is directed to having a relatively low resistance to fluid flow.
- One of the principal obstacles to providing a low resistance to flow characteristic in a conventional check valve is the flow path through the valve mechanism which flow path tends to impinge the valve members and the spring return assembly to thereby add significantly to the resistance of the fluid flow.
- the low resistance to fluid flow of the present invention is in part a function of the improved fluid flow path through the check valve.
- a check valve It is also generally desirable for a check valve to have a high gain characteristic wherein as the pressure is increased to open the check valve, for a unit of pressure increase, the valve opening area also increases by a corresponding incremental amount.
- any pressure increase in the free flow direction causes the valve to approach a maximum opening position with a very small restriction to flow in the free flow direction.
- implementing such a high gain characteristic in a conventional check valve tends to adversely effect the closing rate of the valve with favorable high gain and the valve closing rate being generally inversely related.
- a relatively low spring rate results in a valve mechanism which tends to be driven in oscillation as a result of the natural frequency of the mass of the spring and the valve and the mechanical spring rate of the valve system.
- the hydrodynamic forces which are exerted through the valve also tend to be sinusoidal in nature and thus tend to excite and drive the valve in a natural frequency oscillation.
- Such valve oscillation produces a squealing or chattering condition which is deleterious to valve performance.
- the foregoing instability characteristics inherent in a low rate spring can be overcome by employing a valve spring having a higher spring rate which of course detracts from the high gain characteristics of the valve.
- valve has a relatively low resistance to fluid flow in the free flow direction, has structural features which alleviate adverse silting conditions, has a relatively stable spring system to alleviate valve chatter, has a favorable valve closure rate and has an improved free flow fluid path through the valve.
- the invention in a preferred form is a check valve comprising a generally tubular body which is adapted for mounting in a counterbore of a fluid conduit.
- the body comprises a generally cylindrical base and a guide sleeve of reduced diameter which axially extends from the base.
- the body forms an axially extending fluid passageway and an interior valve seat surrounding the passageway at an intermediate axial location.
- the guide sleeve has a plurality of angularly spaced discharge openings axially spaced from the valve seat and a pair of orifices axially spaced from the valve seat between the valve seat and the openings.
- a valve ball is closely received in the guide sleeve and axially displaceable therein.
- the ball is adapted for seating against the valve seat for sealing engagement therewith.
- a spring assembly axially biases the ball into sealing engagement with the valve seat so that when the force produced by the differential pressure applied to the ball exceeds the opposing force exerted by the biasing means, the ball is axially displaced in the guide sleeve to a position wherein the fluid flow path extends generally axially through the valve seat and into the guide sleeve and thereafter generally radially through the orifices and openings for flow generally exteriorly of the guide sleeve.
- the spring assembly preferably comprises a pair of aligned springs and two damping members interposed between the springs and the ball.
- the spring assembly is axially displaceable in the guide sleeve.
- the damping members are slidably received in the guide sleeve and engage the sleeve to provide an axial damping displacement for the spring assembly.
- the guide sleeve in one form has four equiangularly spaced discharge openings of substantially identical generally rectangular shape, and the orifices are located at diametrically opposed locations of the sleeve at the boundaries of two of the discharge openings with the orifices being dimensioned to have a substantially smaller area than the area of the openings.
- the ball generally intersects the sleeve along a generally circular path for a pre-established axial distance as the ball is axially displaced from the valve seat.
- FIG. 1 is an axial sectional view of a check valve in accordance with the present invention illustrated in combination with a fluid conduit in which the valve has been mounted;
- FIG. 2 is a fragmentary side view of a selected portion of the check valve of FIG. 1;
- FIG. 3 is a fragmentary cross-sectional view of the check valve and fluid conduit taken along the line 3--3 of FIG. 1.
- Check valve 10 is preferably of a compact miniaturized form which is mounted in position in a fluid conduit 12. As further illustrated in FIG. 1, the check valve 10 is inserted into a counterbore 14 having a circumferentially extending tapered shoulder 16. The direction of free flow from an upstream location to a downstream location through the formed fluid passageway and the check valve is generally designated by the arrows in FIG. 1. The broken arrows illustrate the directional flow path subsequent to the opening of the valve.
- Check valve 10 comprises a tubular insert 20 which comprises a plug 22 of enlarged diameter and an axially extending sleeve 24 which integrally extends from the plug.
- the insert is preferably formed from aluminum or stainless steel.
- the exterior downstream end of the plug 22 forms a tapered shoulder 26 which in complementary fashion forcefully seats against the shoulder 16 of the counterbore.
- the plug is exteriorly dimensioned so that the plug is closely received in the enlarged portion of the counterbore.
- a plurality of circumferentially extending axially spaced grooves 28 traverse the exterior surface of the plug to form alternating axially spaced sealing lands and grooves.
- the outside diameter of the sleeve 24 is generally uniform and is less than the diameter of the reduced portion of the conduit bore so that a generally annular passageway is formed in the reduced bore portion between the sleeve 24 and the wall of the fluid conduit 12.
- An enlarged tapered central axially extending bore 30 extends from the upstream end of the plug and communicates with a reduced bore 32 which extends through the opposite end of the plug.
- the check valve 10 is mounted in the fluid conduit by inserting the insert 20 into counterbore 14 so that the shoulder 26 of the plug axially seats against the counterbore shoulder 16.
- a tapered pin (not illustrated) is inserted into the tapered bore 30. The pin and the plug are dimensioned so that as the tapered pin is forcefully axially driven into the plug (to the right of FIG.
- the pin forces the plug to controllably radially expand to thereby force the plug lands to sealingly engage the wall of the fluid conduit 12 in a fashion wherein the edges of the lands bite into the surrounding material of the conduit to form independent seals and retaining rings with the conduit.
- the expanded tapered bore subsequently functions as a fluid inlet passageway when the check valve is mounted in position as illustrated.
- Reduced bore 32 opens into an enlarged uniform bore 34 which axially traverses the length of sleeve 24.
- the upstream end of bore 34 is defined by an annular shoulder 36 which intersects the end of the wall of bore 32 to form a sharp, well-defined continuous circular edge 38 which functions as a valve seat.
- a valve member in the form of a spherical ball 40 is received in bore 34.
- Ball 40 has a diameter which is only very slightly less than the diameter of the bore 34.
- Ball 40 is axially displaceable for sealing engagement with seat 38 to prevent fluid flow through the check valve.
- Ball 40 is normally biased to the closed or seated position of FIG. 1 by a spring assembly designated generally by the numeral 42. In the seated position, the ball also intersects the wall of the bore 34 along a circular path axially spaced from seat 38 to form a quasi-secondary valve seat engagement with sleeve 24.
- Spring assembly 42 includes a follower 44 forming a recess which is contoured to symmetrically engage against ball 40 to urge (to the left of FIG. 1) the ball to the closed seated position.
- the follower 44 has a cylindrical surface with a diameter which is approximately commensurate with the diameter of bore 34.
- follower 44 is slidably received in sleeve 24 and axially displaceable therein.
- a central bore 46 extends axially through the follower to provide a vent passage so that the ball may be firmly engaged against the follower.
- the downstream end of the follower forms a central axially opening recess 48.
- the recess 48 defines a retainer for receiving one end of a coil spring 50.
- the other end of coil spring 50 is captured in a retainer recess of an axially displaceable damping member 52.
- Damping member 52 contains an opposing, axially spaced retainer recess for capturing an end of a second coil spring 60.
- the damping member 52 has a generally cylindrical surface which is closely received by sleeve 24 to permit a restricted damped axial movement of the damping member 52.
- a damping bore 54 extends through the damping member 52 coaxially with the sleeve 24.
- a generally cup-shaped end cap 62 is received at the downstream end of sleeve 24 and welded in fixed position to the sleeve. End cap 62 forms a retainer recess for fixably seating the opposite downstream end of spring 60. Cap 62 also contains a central damping bore 64 which axially aligns with the corresponding axially spaced damping bore 54. The damping bores 54 and 64 have generally equal diameters and cooperate with bore 34 to form a damping passage through the spring assembly 42.
- Springs 50 and 60 are relatively short springs which are substantially identical and have a relatively low spring rate and low preload force.
- An exemplary spring rate is 0.4 lbs. per inch for each spring.
- the dual spring configuration has an effective spring rate of 0.2 lbs. per inch.
- the dual spring configuration adds stability to the check valve while also allowing for sufficient axial displacement of ball 40 as described hereinafter.
- the damping member 52 functions as a guide member to prevent intermediate spring buckling or deformation that results from employing an equivalent single longer spring having a small pre-load force.
- the intermediate axially displaceable damping member 52 in cooperation with springs 50 and 60 functions to provide a damping mechansim to thereby minimize or alleviate deleterious oscillations and chatter in the valve mechanism.
- sleeve 24 Four equiangularly spaced, substantially identical discharge windows 70, 72, 74 and 76 are formed in sleeve 24.
- the foregoing windows have a generally rectangular shape and are axially positioned so that the upstream terminus of the windows is axially spaced downstream from the intersection of the ball 40 and the inner wall of the sleeve 24 when the ball is seated against seat 38.
- a pair of diametrically opposed notches at an intermediate location of the upstream boundaries of windows 70 and 74 form a pair of opposed pilot orifices 80 and 82.
- the upstream terminus of the orifices is axially spaced from the intersection of the ball 40 with the sleeve 24 in the seated closed valve position.
- the pilot orifices are dimensioned to provide both a significantly smaller opening in the sleeve than the windows to increase the discharge velocity through the pilot orifices, and an opening of sufficient size to readily pass silt or contamination particles in the fluid traversing the valve--even at low fluid flow rates.
- the diameters of the pilot orifices are each approximately 0.008 inches, and the discharge windows each have an axial length of approximately 0.080 inches.
- a positive fluid pressure differential in the free flow direction of the arrows forces ball 40 to unseat and to be axially displaced (toward the right of FIG. 1).
- the positive pressure differential initially displaces the ball axially until the intersection of the sleeve with the circumference of the ball is axially displaced beyond the pilot orifices 80 and 82. Once the ball uncovers the orifices, the released fluid is initially propelled generally radially through the orifices.
- the pressure differential increases, the ball will be further axially displaced to allow a relatively greater volume of fluid flow through the discharge windows 70, 72, 74 and 76.
- the resulting fluid flow path through the check valve (as illustrated by the broken arrows) extends initially generally axially through the valve seat and then generally radially through the pilot orifices and discharge windows to form a generally unobstructed flow path of annular cross-section between the outer surface of the cylindrical sleeve 24 and the inside wall of the adjacent conduit 12. Consequently, a relatively low resistance to fluid flow can be effectively implemented since the flow path is generally diverted from the region of the spring assembly 42.
- the quasi-secondary valve seat formed at the intersection of the ball and the sleeve wall is effectively maintained for a pre-established axial distance even though the ball is displaced from seat 38.
- no more than a very small volume of fluid passes beyond the upstream side of the ball in the free flow direction.
- silting at the valve seat can be effectively eliminated.
- the pilot orifices are dimensioned so that the silt particles will be forcefully expelled through the orifice openings even at relatively low flow rates.
- the opening through valve seat 38 is sufficiently large that the silt particles do not accumulate or collect at the valve seat.
- the spring assembly 42 functions to provide favorable gain and stability characteristics for check valve 10.
- the implemented multi-spring system is equivalent to a single long low rate spring.
- the equivalent multi-spring assembly will not deform or buckle at the mid-point as may occur with the single long low rate spring.
- the intermediate damping member or members function as a guide to prevent buckling of the spring assembly.
- Two spring cavity damping chambers 90 and 91 are formed within spring assembly 42.
- a minimal sliding clearance between the damping member 52 and the sleeve 24 causes the fluid in chambers 90 and 91 to be interconnected via damping bore 54 and the fluid in chamber 91 to be interconnected with the downstream fluid via damping bore 64. Consequently, axial movement of the damping member in either the upstream or downstream direction is inhibited by the fluid resistance of the damping bores.
- the dimensions of bore 54 may be decreased to enhance the damping and increased to reduce the damping.
- the damping members primarily function as a stabilizing element between the springs to prevent the valve from oscillating at or near its natural frequency or some other frequency due to hydrodynamic oscillations at the ball and seat.
- check valve 10 is a valve of very compact form which has a low resistance to fluid flow in the free flow direction and consequently a high gain characteristic.
- the axial length of insert 20 is approximately 0.6 inches and the outside diameter of plug 22 is approximately 0.2 inches.
- the ball and seat valving configuration in combination with the tubular ball guide, the discharge window locations and the pilot orifice locations forces the valve member to open a substantial axial distance at relatively low flow pressures to thereby eliminate or minimize silting or contamination conditions.
- the valve is also very stable because of the second order damping provided by the multiple spring assembly and damping chambers 90 and 91.
- the substantially radial flow path presents a relatively unobstructed flow path through the check valve and further enhances the low flow resistance of the check valve.
Abstract
Description
Claims (11)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US06/846,962 US4706705A (en) | 1986-04-01 | 1986-04-01 | Check valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US06/846,962 US4706705A (en) | 1986-04-01 | 1986-04-01 | Check valve |
Publications (1)
Publication Number | Publication Date |
---|---|
US4706705A true US4706705A (en) | 1987-11-17 |
Family
ID=25299433
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US06/846,962 Expired - Lifetime US4706705A (en) | 1986-04-01 | 1986-04-01 | Check valve |
Country Status (1)
Country | Link |
---|---|
US (1) | US4706705A (en) |
Cited By (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5121947A (en) * | 1991-02-08 | 1992-06-16 | The Lee Company | Expansion sealing device |
EP0640783A1 (en) * | 1993-08-23 | 1995-03-01 | Francine Schneider | High pressure check valve |
US5404905A (en) * | 1994-04-25 | 1995-04-11 | Lauria; Thomas J. | Backflow preventer with failure indicator |
US5462082A (en) * | 1994-10-07 | 1995-10-31 | Lauria; Thomas J. | Backflow preventer with failure indicator |
WO1996031285A1 (en) * | 1995-04-05 | 1996-10-10 | Campbell Hausfeld/Scott Fetzer Co. | Airless paint sprayer outlet check valve |
US6138457A (en) * | 1998-02-27 | 2000-10-31 | Applied Power Technology Incorporated | Combustion powered cooling system |
FR2803052A1 (en) * | 1999-12-24 | 2001-06-29 | Bosch Gmbh Robert | PRESSURE REGULATING VALVE AND METHOD FOR MANUFACTURING SUCH A VALVE |
FR2803053A1 (en) * | 1999-12-24 | 2001-06-29 | Bosch Gmbh Robert | PRESSURE REGULATING VALVE AND METHOD FOR MANUFACTURING SUCH A VALVE |
WO2002053957A1 (en) * | 2000-12-29 | 2002-07-11 | Chang-Hyeon Ji | Leak control valve |
US6513545B2 (en) | 2001-01-16 | 2003-02-04 | Evan M. Rhone | Safety valve with adjustable maximum flow shut off mechanism |
US6622752B2 (en) * | 2000-06-16 | 2003-09-23 | Bosch Automotive Systems Corporation | Pressure relief valve |
US20050232821A1 (en) * | 2003-09-19 | 2005-10-20 | Carrillo Albert L | High density plate filler |
WO2006134264A1 (en) * | 2005-06-15 | 2006-12-21 | Eaton | Pressure relief device |
US20070014694A1 (en) * | 2003-09-19 | 2007-01-18 | Beard Nigel P | High density plate filler |
US20070284553A1 (en) * | 2006-06-09 | 2007-12-13 | Honeywell International, Inc. | Valve ball guide and seat design |
US7407630B2 (en) | 2003-09-19 | 2008-08-05 | Applera Corporation | High density plate filler |
US20080314449A1 (en) * | 2007-06-22 | 2008-12-25 | Bendix Commercial Vehicle Systems Llc | Check valve |
US20090183782A1 (en) * | 2008-01-21 | 2009-07-23 | Martin Francis J | Pressure relief valve with singular body |
EP2085659A1 (en) * | 2008-02-01 | 2009-08-05 | GM Global Technology Operations, Inc. | Automatic transmission |
US20110123376A1 (en) * | 2009-02-20 | 2011-05-26 | Aritomi Shunsuke | High-Pressure Fuel Supply Pump and Discharge Valve Unit Used Therein |
US20110129363A1 (en) * | 2007-08-08 | 2011-06-02 | Toyota Jidosha Kabushiki Kaisha | Fuel pump |
US7998435B2 (en) | 2003-09-19 | 2011-08-16 | Life Technologies Corporation | High density plate filler |
CN102563136A (en) * | 2011-12-16 | 2012-07-11 | 杭州春江阀门有限公司 | Low-resistance non-return valve |
US8277760B2 (en) | 2003-09-19 | 2012-10-02 | Applied Biosystems, Llc | High density plate filler |
CN102996433A (en) * | 2012-10-31 | 2013-03-27 | 镇江宝城注浆设备有限公司 | Grouting pump safety valve |
CN103225704A (en) * | 2012-01-31 | 2013-07-31 | 株式会社电装 | Check valve and braking system using the same |
CN103225703A (en) * | 2012-01-31 | 2013-07-31 | 株式会社电装 | Check valve |
WO2014183898A1 (en) * | 2013-05-17 | 2014-11-20 | Robert Bosch Gmbh | Non-return valve |
CN104428533A (en) * | 2012-06-28 | 2015-03-18 | 罗伯特·博世有限公司 | Piston fuel pump |
US20150300353A1 (en) * | 2014-04-19 | 2015-10-22 | Emerson Climate Technologies, Inc. | Pulsation dampening assembly |
US9200717B2 (en) | 2008-01-21 | 2015-12-01 | Ausco, Inc. | Pressure relief valve with singular body |
US20160305384A1 (en) * | 2015-04-20 | 2016-10-20 | Hitachi, Ltd. | Automotive fuel pump |
US9482354B2 (en) | 2014-04-15 | 2016-11-01 | Girard Equipment, Inc. | Super high flow pressure relief vent |
US20170009900A1 (en) * | 2014-04-24 | 2017-01-12 | Kyb Corporation | Relief valve |
CN107208591A (en) * | 2015-01-26 | 2017-09-26 | 日立汽车系统株式会社 | Valve system and the high-pressure fuel feed pump with it |
US20180347716A1 (en) * | 2015-09-25 | 2018-12-06 | Bloechlinger Engineering Ag | Check valve |
CN110529635A (en) * | 2019-07-16 | 2019-12-03 | 郑州轻工业学院易斯顿美术学院 | Valve gear |
EP3798428A1 (en) * | 2019-09-30 | 2021-03-31 | RD Estate GmbH & Co. KG | Valve for controlling and / or regulating a fluid flow |
US20230029119A1 (en) * | 2020-01-07 | 2023-01-26 | Hitachi Astemo, Ltd. | Discharge valve mechanism and high-pressure fuel supply pump including the same |
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US3589386A (en) * | 1969-09-02 | 1971-06-29 | Air Con Inc | Pilot valve |
US3746038A (en) * | 1971-01-25 | 1973-07-17 | Parker Hannifin Corp | Fuel head compensating valve for fuel injection nozzle |
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JPS5594070A (en) * | 1979-01-08 | 1980-07-17 | Shin Meiwa Ind Co Ltd | Flow control valve |
-
1986
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Patent Citations (12)
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US1094267A (en) * | 1913-10-08 | 1914-04-21 | Hiram E Sullivan | Check-valve. |
US1798631A (en) * | 1926-05-14 | 1931-03-31 | Calvin J Mummert | Pressure-equalizing valve |
US2431769A (en) * | 1943-04-30 | 1947-12-02 | Parker Appliance Co | Quick opening check valve assembly |
US2632458A (en) * | 1946-04-12 | 1953-03-24 | Goodman Mfg Co | By-pass valve |
US2858838A (en) * | 1955-11-10 | 1958-11-04 | Scaramucci Domer | Drill pipe float valve |
US3072144A (en) * | 1961-05-25 | 1963-01-08 | Flowmatic Controls Inc | Valve with damping system |
US3347266A (en) * | 1963-09-19 | 1967-10-17 | Gen Dynamics Corp | Spring biased relief valve |
US3375844A (en) * | 1963-12-18 | 1968-04-02 | Mercier Jean | Unloader valve |
US3589386A (en) * | 1969-09-02 | 1971-06-29 | Air Con Inc | Pilot valve |
US3746038A (en) * | 1971-01-25 | 1973-07-17 | Parker Hannifin Corp | Fuel head compensating valve for fuel injection nozzle |
US3894556A (en) * | 1974-01-02 | 1975-07-15 | Lear Siegler Inc | Pressure limiting valve |
JPS5594070A (en) * | 1979-01-08 | 1980-07-17 | Shin Meiwa Ind Co Ltd | Flow control valve |
Cited By (61)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5121947A (en) * | 1991-02-08 | 1992-06-16 | The Lee Company | Expansion sealing device |
EP0640783A1 (en) * | 1993-08-23 | 1995-03-01 | Francine Schneider | High pressure check valve |
US5404905A (en) * | 1994-04-25 | 1995-04-11 | Lauria; Thomas J. | Backflow preventer with failure indicator |
US5462082A (en) * | 1994-10-07 | 1995-10-31 | Lauria; Thomas J. | Backflow preventer with failure indicator |
US5609300A (en) * | 1995-01-09 | 1997-03-11 | Campbell Hausfeld/Scott Fetzer Company | Airless paint sprayer outlet check valve |
WO1996031285A1 (en) * | 1995-04-05 | 1996-10-10 | Campbell Hausfeld/Scott Fetzer Co. | Airless paint sprayer outlet check valve |
US6138457A (en) * | 1998-02-27 | 2000-10-31 | Applied Power Technology Incorporated | Combustion powered cooling system |
FR2803053A1 (en) * | 1999-12-24 | 2001-06-29 | Bosch Gmbh Robert | PRESSURE REGULATING VALVE AND METHOD FOR MANUFACTURING SUCH A VALVE |
US6439263B2 (en) * | 1999-12-24 | 2002-08-27 | Robert Bosch Gmbh | Pressure regulating valve and method for producing a pressure regulating valve |
FR2803052A1 (en) * | 1999-12-24 | 2001-06-29 | Bosch Gmbh Robert | PRESSURE REGULATING VALVE AND METHOD FOR MANUFACTURING SUCH A VALVE |
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